Coin handling and changing device



Feb. 20, 1968 w. H. CALLAHAN ETAL 3,369,641

COIN HANDLING AND CHANGING DEVICE Filed March 21, 1966 5 Sheets-Sheet l I INVENTORS I26" l0 WILL/AM H. CALLAHAN T, /20 /4 /22 //a //0 ROYAL 1? 1 w. H. CALLAHAN ETAL- 3,

COIN HANDLING AND CHANGING DEVICE Filed March 21, 1966 r 5 Sheets-Sheet 2 /NVE/VTOR$ I WILLIAM H. cALLAHA-A/ ROYAL E SMITH Feb. 20, 1968 v w. H. CALLAHAN ETAL COIN HANDLING AND CHANGING DEVICE.

5 Sheets-Sheet 5 Filed March 21, 1966 INVENTOR. W/LLAM H. CALLAHAN ROYAL F. SMITH Feb. 20, 1968 w. H CALLAHAN ETAL 3,

COIN HANDLING AND CHANGING DEVICE 5 Shee tsSheet 4 Filed March 21, 1966 //VVE/VTORS. W/LL/AM H. CALLAHAN ROYAL E .5

Feb. 20, 1968 W. H. CALLAHAN ETAL.

Filed March 21, 1966 5 Sheets-Sheet 5 l MANUAL PAYOUT W/LL/AM H.

VEND MOTOR INVENTORS. CALLAHAN ROYAL ESMI TH z-1 lf/2 PAYOUT RELAY E O- I I I- SE LERRT |o l N com 1 1f 'awa'r L l |o PRICE o "g LsELEcmR L2 |5 PRICE 90 E; 7\48@ 5ac E I 1 COIN L2 25 PRICE MI {SELECTOR 553 com L2 ;REJECT United States Patent 3,369,641 COIN HANDLING AND CHANGING DEVICE William H. Callahan and Royal F. Smith, Aurora, Ill.,

assignors t0 Lektro-Vend C0rp., Aurora, 111., a corporation of Delaware Filed Mar. 21, 1966, Ser. No. 536,137 18 Claims. (Cl. 194-2) ABSTRACT OF THE DISCLOSURE A vending machine having a segmented indexable stepping drum with a cam surface on each of the segments, and a plurality of cam followers adapted to be actuated by said cam surfaces. The cam followers in turn actuate stepping switches and exact price switches. A single solenoid rotates the drum uni-directionally and cocks it to register credit for the amount of money inserted] Customer product selection energizes payout-and subtract cams, the latter being linked to the stepping switches cam followers and moving the same in said one direction to subtract the purchase price from the established credit.

The invention relates generally to money actuated devices and more particularly to improvements in coin operated devices of the type which are employed in vending machines and are capable of dispensing products and giving change.

Coin handling and changing devices of the type under consideration are old and well known to the art. Such devices are most frequently employed in electrically operated vending machines which are capable of dispensing a number of different items at a variety of prices. A typical vending machine might dispense various candies and pastries bearing four difierent prices such as and The function of the coin handling and changing device is of course to dispense the article selected by the customer and also to return change in the event the amount deposited is greater than the cost of the article vended.

In general, the prior art devices comprised a coinactuated pulse generator which transmitted a number of electrical pulses corresponding to the units (such as nickels) of money inserted, a circuit step-ping assembly which was actuated by the pulse generator and served to prime the entire device in response to the inserted money, and a series of cams or other mechanical members which operated, upon selection of a particular article by the no coins in the change making section, rejecting slugs,

etc.

As will be appreciated by those versed in the art, the heart or nerve center of the coin handling devices in question is the described circuit stepping assembly. These assemblies invariably comprised a number of cams which Were adapted to rotate about a common axis. As will likewise be appreciated by those versed in the art, it is necessary to return the stepping cams to a zero or standby position at the end of each vending cycle. It was in the described functions of the circuit stepping assemblies that the prior art devices presented the greatest problems.

Most of the prior ar problems alluded to resulted from the fact that it was believed necessary to rotate the stepping cams in a second, or opposite, direction to achieve the required start position. As a result of this two-directional rotation, a number of complex electrical circuits and expensive par-ts such as relays and the like were required. In addition to the great complexity and cost, the two-directional rotation of the stepping cams frequently resulted in erratic or nonuniform pulsing of said cams. Thus, for example, whereas the insertion of a dime might ordinarily require the rotation 'of the stepping cams through two fixed steps or increments, the lack of positive uni-directional control over the cams might undesirably permit the rotation thereof through three increments. In such a case, the customer might receive more change than he was entitled to. Other disadvantages of the prior two-directional systems were the greatly increased size of the devices in which they were incorporated, the frequency of breakdowns and the need for relatively skilled people to assemble and service the devices.

It is therefore an important object of this invention to provide a coin handling and changing device which overcomes all of the disadvantages described hereinabove.

Another object is to afford a coin handling and changing device of the character described which employs a novel circuit stepping assembly which rotates only in a single direction. A related object is to afford such a device having positive uni-directional control over the rotation of the stepping cams so that uniform movement thereof through the exact number of required increments is assured.

A further object is to provide a coin handling and changing device of the character described which eliminates many costly members, such as a plurality of electrical relays, which were heretofore required.

Still another object is to afford a coin handling and changing device of the character described which is greatly reduced in overall size.

Yet another object is to provide a coin handling and changing device of character described having means for readily adjusting the circuit stepping assembly to operate with a variety of pricing programs as desired.

Still a further object is to afford a coin handling and changing device of the character-described having exact price means for preventing vending of merchandise when there are no coins available for change, but permitting vending of merchandise when the exact price of the article selected is inserted. A related object is to afford such a device in which said exact price means is physically coupled to the circuit stepping assembly and operates automatically as a part thereof.

Yet a further object is to provide a coin handling and changing device of the character described having escrow means for insuring that a supply of unit coins (generally nickles) is always diverted to a reservoir in readiness for making change. A related object is to provide a device of the character described in which said escrow means likewise functions to divert excess coins to a cash box or to a money return chute as particular conditions demand.

Another object is to provide a coin handling and changing device of the character described which is greatly simplified in construction, operation and maintenance and yet is most durable and efficient for the purposes intended.

For the purpose of facilitating an understanding of our invention, we have illustrated in the accompanying drawings, a preferred embodiment thereof, from an inspection of which. when considered in connection with the fo1lowing description, our inventiOn, its mode of construction. assembly and operation, and many of its advantages should be readily understood and appreciated.

Referring to the drawings in which the same characters of reference are employed to indicate corresponding or similar parts throughout the several figures of the draw- 1ngs:

FIG. 1 is a front elevational view of a coin handling and changing device embodying the principles of the ina) vention, with portions broken away and in section, to show the relationship of the various parts thereof;

FIG. 2 is an enlarged perspective view of the circuit stepping drum showing the relative positions of the various cams thereon when the device is in the standby or zero condition;

FIG. 3 is an exploded view of the stepping drum and showing the relationship thereto of the cooperating stepping levers and exact price levers;

FIG. 4 is a fragmentary top plan view of the stepping drum and associated stepping levers and illustrating the Y-shaped linkage of said levers to the subtract cam in disconnected position;

FIG. 5 is an enlarged fragmentary sectional view taken on the plane of line 5-5 in FIG. 4 and viewed in the direction indicated;

FIG. 6 is a similar view taken on the plane of line 6--6 in FIG. 4 and viewed in the direction indicated;

' FIG. 7 is a similar view taken on the plane of line 77 in FIG. 4 and viewed in the direction indicated;

FIG. 8 is a schematic representation of the relative positions of the stepping cams and associated stepping levers and exact rice levers when the device is in the standby condition and illustrating graphically the relationship of successive step positions;

FIG. 9 is an exploded fragmentary perspective view showing the various elements of the escrow and payout assemblies;

FIG. 10 is a sectional view taken on the plane of line 1010 in FIG. 9 and viewed in the direction indicated;

FIG. 11 is an enlarged fragmentary end elevational view taken on the plane of line 1111 in FIG. 1 and viewed in the direction indicated; and

FIG. 12 is a schematic view showing the electrical circuitry of the invention, with those portions not specifically described herein being enclosed in dotted outline.

Turning now to FIG. 1 of the drawings, the reference numeral 10 indicates generally a coin handling and changing device embodying the principles of the invention. The device 10 comprises a pulse generator 12 which transmits an electrical pulse for each unit of money inserted into the device. Thus, for example, if the coin unit is a nickel, the generator 12 will transmit one pulse for a nickel, two pulses for a dime and five pulses for a quarter. Such generators are well known to the art and may comprise a device of the type shown in US. Patent No. 3,182,780.

A circuit stepping assembly indicated generally by the numeral 15 is activated in response to the pulses of the generator 12. The stepping assembly 15 comprises a solenoid 16 which is connected electrically to the generator 12, said solenoid including an armature 18. A stepping assembly driver is pivotally connected to the armature 18 for movement therewith. As shown in FIG. 5 of the drawings, the driver 20 comprises a notch 22 in the upper surface thereof and a depending tooth 24, whose functions will become apparent as the description proceeds.

Associated with the driver 20 is a stepping drum which is indicated generally by the reference character 30 (see FIG. 2). The drum 30 comprises a cylindrical member 32 having a plurality of stepping cams 35a, 35b, 35c and 35d positioned on the surface thereof. In addition to the stepping cams 35, there is a zero or standby cam 36 positioned on the surface of the drum 30. Completing the drum structure is an enlarged diameter ratchet wheel 38 having a plurality of equally spaced teeth 40. The drum 30 may comprise an integrally formed member but, as indicated in FIG. 2 of the drawings, the same preferably comprises a plurality of individual drum segments which are operatively connected together by mating indexing teeth. In this manner, the stepping cams 35 may be indexed to accommodate any desired pricing program, although in the embodiment illustrated, the same are programmed for 5d, 10, 15 and The drum is rotatably mounted on a shaft 42 and positioned so that the ratchet wheel 38 is in vertical alignment with the driver 20. Referring to FIG. 5, it will be seen that the driver 20 is biased by a spring 43 and urged toward the left by a link and spring assembly 41, so that the depending tooth 24 operatively engages the ratchet teeth 40. Each time the driver 20 moves to the left as viewed in FIG. 5 in response to the stroke of the solenoid armature, the ratchet wheel 38 is caused to rotate counterclockwise through a step or increment equal to the angular length of one tooth 40. In this regard, a stop pin 23 is provided and the same cooperates with the notch 22 to positively limit the length of the drivers stroke. Immediately after such an incremental rotation, the armature 18 begins its return stroke whereupon the action of the assembly 41 and the biasing spring 43 causes the tooth 24 to drop down and engage the next succeeding tooth 40. Thus, each stroke of the driver 20 rotates the ratchet wheel 38 one step.

From the described operation of the driver 20 and ratchet wheel 38, it will be appreciated that each incremental rotation of the wheel is done under the positive urging and control of the driver. As a result, the ratchet wheel invariably is caused to rotate only the exact number of counterclockwise steps corresponding to the number of pulses emitted by the pulse generator 12. In this respect, it will likewise be noted that a spring biased pawl 44 is provided to cooperate with the ratchet wheel 38 and further insure that the same rotates only in the described uni-directional manner.

In the embodiment illustrated, the ratchet wheel 38 has twenty-six (26) teeth spaced equally therearound so that the angular distance of the step or increment between each adjacent pair of teeth is about 13.85 degrees. The stepping cams 35 are directly related dimensionally to the step between the ratchet teeth 40. Thus, each of said cams is equal in arcuate length to fourth of such steps. Stated otherwise, a cam follower will ride on any of the cams 35 for four pulses of the pulse generator 12. On the other hand, the arcuate length of the standby cam 36 is equivalent to only one incrementional step. The reasons for the described particular dimensions of the cams 35 and 36 will become clear in the ensuing description.

Referring now to FIGS. 3, 4 and 7, it will be seen that stepping levers 45a, 45b, 45c and 45d are associated respectively with stepping cams 35a, 35b, 35c and 35d, each of said levers being provided with a cam follower 46a, 46b, 46c and 46d. Stepping switches 48a, 48b, 48c and 48d are associated respectively with the levers 45a, 45b, 45c and 45d and are adapted to be actuated thereby in the customary manner indicated. In similar fashion, a zero lever 58 having a cam follower 52 is associated with the zero cam 36. The zero lever is pivotally mounted on a shaft 53 and a zero switch 54 is associated with said lever and adapted to be actuated thereby.

Also associated with the stepping cams 35a, 35b, 35c and 35d are a series of respective exact price levers 55a, 55b, 55c, and 55d, said levers having cam followers 56a, 56b, 56c and 56d. The exact price levers 55 are pivotally mounted on a shaft 57 and are adapted to actuate respective exact price switches 58a, 58b, 58c and 58d. It will thus be appreciated that when the stepping cams 35 rotate, they simultaneously affect the stepping levers 45 and exact price levers 55, which levers in turn actuate their respective electrical switches 48 and 58.

As seen in FIGS. 1 and 4 of the drawings, the stepping levers 45 are pivotally mounted on a common shaft 60. A tension spring 62 is connected to the shaft 60 and adapted to normally urge the same downwardly. Likewise connected to the shaft 60 are supporting links 63, 63 and a Y-shaped linkage member having arms 64 and 66. The linkage arms 64 and.66 are in turn connected to a payout assembly indicated generally by the reference numeral 70.

The payout assembly comprises a subtract lever 72 which is pivotally connected to the linkage arms 64 and 66 as at 74. The opposite end of the subtract lever 72 is pivotally connected as at 76 to the supporting housing of the device 10. Intermediate the pivot points 74 and 76, the subtract lever 72 carries a cam follower 78 which is of course normally urged downwardly by the spring 62 through the link arms 64 and 66.

Cooperating with the subtract lever 72 is a step subtract cam 80 which is mounted on the drive shaft 82 of a suitable motor M1 (see FIG. 12) for clockwise rotation as viewed in FIG. 1 of the drawings. The step subtract cam 80 is formed with four arcuate camming surfaces 84a, 84b, 84c and 84d which are of successively decreasing radius from the center of the drive shaft 82. The radial decrease between successive camming surfaces 84 is directly related to the arcuate step between adjacent ratchet wheel teeth 40. Thus, one complete revolution of the subtract cam 80 will cause the shaft 60 carrying the stepping levers 45 to move four steps downwardly. Since the respective cam followers 46 bear against the cams 35 or the surface of the drum 32, these members are caused to travel through an arcuate distance of four steps. The significance of this motion will become apparent when the operation of the entire device is subsequently discussed.

A boss 86 projects outwardly from the subtract cam 80 and is adapted to actuate a cycle switch 88 and a reset switch 90 during each revolution of the subtract cam. The function of the cycle switch 88 is to insure energization of the motor so that the subtract cam 80 will make a complete revolution with the initiation of each cycle, irrespective of what occurs in the other circuits of the device. The function of the reset switch 90 is to pulse or initiate the reset cycle for returning the stepping assembly to the zero position after completion of a payout or vend cycle. Also projecting outwardly from the sub tract cam 80 is a stub shaft 92 whose function will become clear as the description proceeds.

Mounted on the motor shaft 82 for unison rotation with the subtract cam 80 is a payout cam 95. The payout cam 95 is provided with four substantially right angle-shaped camming notches 96 which are designed to impart a reciprocating motion to a cooperating cam follower. A bifurcated payout lever 98 is pivotally connected to the housing of the device at a point intermediate its length, such as at 100. At its upper end, the payout lever 98 carries a rotatable cam follower 102 which is adapted to cooperate with the payout cam 95. The cam follower 102 is normally urged into bearing relationship with the payout cam by a spring 104.

As in the case of the subtract cam surfaces 84, the spacing and dimensions of the payout carn surfaces 96 are directly related to the step between adjacent ratchet Wheel teeth 40. It is important to note however that the cam follower 102 is positioned so that it does not reach the first cam surface 96 until the cam follower 78 is recahing its second cam surface 84b. In other words, there is a one step time lag before the payout cam becomes effective.

At its lower end, the payout lever 98 carries a roller 106 which is operatively engaged with a payout slide 110. The payout slide 110 comprises a horizontal plate 112 and a vertical plate 114, said vertical plate being formed with a notch 116 for receiving the roller 106 therein. The horizontal plate 112 has a nickel receiving opening 118 formed therein adjacent one end thereof (see FIG. 9). At its opposite end, the plate 112 has a short upstanding flange 120. The payout slide 110 rides upon a base plate 122 which plate is formed with a nickel discharge opening 124 therein. It will thus be appreciated that when the payout slide is moved so that the nickel receiving and discharge openings 118 and 124 are in alignment, any nickel which previously had been positioned in the opening 118 will fall through the opening 124 from whence it may be carried to the customer.

A payout solenoid 126 having an armature 128 is positioned adjacent the payout slide 110. The armature 128 carries a blocking plate 130 which, as indicated in FIG.

1, is normally in the path of travel of the slides upstanding flange 120. Thus, unless the blocking plate is retracted, the same will prevent full travel of the payout slide to the left and thereby further prevent the discharge of any nickels through the discharge opening 124.

Nickels for change are retained in a vertical coin storage tube 132 whose bottom edge abuts the horizontal slide plate 112. When the nickel receiving opening 118 is in alignment with the tube 132, a nickel will obviously fall thereinto. The tube 132 is formed with a slot 134 adjacent its lower end and said slot accommodates therethrough the end portion of a tube empty sensor 136 which is adapted to actuate a tube empty switch 138. The tube 132 is similarly formed with a slot 140 adjacent the upper end thereof for accommodating therethrough a tube sensor 142 (see FIG. 11). The tube full sensor 142 is pivotally mounted at 144 and carries at its upper end an angular diverter arm 146 whose function will subsequently be disclosed.

An escrow assembly indicated generally by the numeral 150 is provided for diverting coins to the cash box or back to the customer as particular conditions demand, and also for insuring that some nickels will always be diverted into the storage tube 132 for change making purposes. Turning to FIGS. 9-11 of the drawings, it will be seen that the escrow assembly 150 comprises a nickel passageway 152 which is adapted to physically retain therein up to two nickels. All other coins (dimes and quarters) and nickels in excess of two which are inserted by any given customer will automatically be diverted by. suitable channeling means (not shown) onto an escrow table to be described. A nickel escrow coil 154 is mounted adjacent the nickel passageway 152 as indicated. Associated with the coil 154 is a nickel escrow gate 156 which is normally urged by a spring 158 into the passageway 152 to pre-" vent passage therefrom of the one or two captive nickels into the storage tube 132 which is positioned therebeneath. However, when the coil 154 is energized, the magnetic field draws the gate 156 out of the passageway to permit free passage of the nickels therefrom.

It will also be seen that a full condition of the tube 132 will cause the sensor 142 to pivot outwardly so that its angular diverter arm 146 enters and blocks the passageway 152. When this occurs, the diverter am 146 of course prevents further passage of nickels into the full storage tube and instead diverts them onto an escrow table 160 which is slidably supported by nails 162 and 164 positioned at opposite ends thereof. A yolk member 166 is secured transversely to the table 160 and in depending relationship therewith. A pair of parallel support arms 168, 168 is pivotally connected to the yolk 166 by suitable means such as connecting shaft 169. It will thus be appreciated that the table 160 is capable of pivotal movement about theshaft 169.

Journalled through the support arms 168 adjacent their lower ends is a pivot shaft 170 whose opposite ends are journalled suitable supporting walls 172 and 174, fragments of which are indicated in exploded FIG. 9. A hearing shaft 176 is likewise journalled through the support arms 168 intermediate the length thereof, and the opposite ends of said shaft are slidjably received in a pair of aligned arcuate slots 178, 178 formed in the walls 172 and 174. It will thus be seen that the support arms are capable of pivotal movement about the pivot shaft 17 0.

When the bearing shaft 176 is resting at the apex of the slots 178 as shown, the table 160 is in the horizontal or neutral position. However, arcuate movement of the bearing shaft 176 to the right end of the'slots 178 causes the table to slide olf of the rail 162 and simultaneously pivot counterclockwise because of the described double pivot support thereof. Such motion of the escrow table results in any monies thereon being returned to the customer. In similar fashion, arcuate movement of the hearing shaft 176 to the left end of the slots 178 causes the table to slide oif of the rail 164 and pivot clockwise. In this instance, any monies on the table fall into the cash box (not shown).

In order to :achieve the described tilting of the table 160 toward the cash box, there is provided an escrow cash box drive assembly 180. The assembly 180 comprises a rocker plate 182 which is pivotally connected at 184 to the wall 172. At its lower end, the plate 182 is provided with a finger 186 and a claw 188. Spring means 190 normally bias the finger 186 into engagement with the pivot shaft 170 so that said plate does not affect the neutral positioning of the bearing shaft 176. At its opposite end, the plate 182 has a substantially right angle arm 192, and said arm is pivotally linked to the subtract cam 80 through a connecting pin 194, a link arm 196 and the stub shaft 92. It will thus be seen that rotation of the subtract cam in the clockwise direction indicated likewise results in a clockwise rotation of the plate 182. When this occurs, the claw 188 engages the shaft 176 and moves the same arcu'ately to the left end of the slots 178.

An escrow return drive assembly 200 is provided for tilting the table 160 clockwise to return money to the customer. The assembly 200 comprises a similar, but reversed, rocker plate 202 which is pivotally connected at 204 to the supporting wall 174. The plate 202 is provided with a finger 206 and a claw 208. A spring 210 normally urges the finger 206 into engagement with the pivot shaft 170. Pivotally connected to the plate 202 adjacent the upper end thereof is a return link 212. The opposite end of the link 212 is connected to the armature of an escrow return solenoid 215. Accordingly, when the solenoid 215 is energized and its armature retracted, the rocker plate 202 is caused to rotate counterclockwise whereupon the claw 208 engages the shaft 176 to move the same arcuately to the right end of the slots 178.

To provide for the situation in which a customer might [insert one or two nickels while the storage tube 132 is not full, and then seek return of his money without making a purchase, there is provided an elongated actuator spring 216. A rod 218 is loosely received through the coils of the sprng 216 so that said spring is capable of torsional rotation about said rod. The bottom of the rod 218 is pivotally supported in a bracket 219 which projects outwardly fom the wall 174, and the bottom wing 217 of the spring is connected to the link 212 in the manner indicated. The upper or free end of the spring 216 terminates in an actuator Wing 220 which is normally positioned somewhat spaced from the tube full sensor 142. As the link 212 is moved to the left, it carries with it the connected bottom Wing of the spring 216 and causes torsional rotation of said spring. The wing 220 thereupon strikes the sensor 142 and pivots the same so that the angular diverter arm 146 enters and blocks the passageway 152. Thus, the nickel or nickels held in the passageway are prevented from .going into the storage tube and are instead diverted to the escrow table 160 for return to the customer.

Upon completon of the vend and/or payout cycle, a reset cycle is required to return the stepping assembly 15 to the zero position. Such a reset cycle is initiated by the momentary closing of the reset switch 90 which is actuated by the boss 86 as the subtract cam 80 is nearing completion of its full revolution. Actuation of the switch 90 causes the solenoid 16 to be energized once again. The driver 20 is of course pulsed so that it rotates the ratchet wheel 38 through one step as previously described. Associated with the driver 20 and adapted to be actuated thereby is a reset interrupter switch 225 (see FIGS. 1, 3 and As the driver 20 moves to the right in response to the return stroke of the solenoid armature 18, the driver drops from a ratchet tooth 40 with which the driver tooth 24 had been engaged, thereby permitting the switch 225 to open. There is thus provided the necessary circuit interruption to operate the solenoid 16. The

pulsing of the solenoid and step-by-step rotation of the ratchet wheel 38 continues until the zero cam 36 raises the cam follower 52 to open the zero switch 54 which deenergizes the solenoid 16. It will of course be observed that the entire reset cycle of the stepping assembly 15 is accomplished with a uni-directional rotation of the drum 30 and under the positive impetus and control of the driver 20.

OPERATION In FIG. 8 of the drawings, there is illustrated a schematic representation of the cooperation and interaction between the stepping cams 35 and the stepping cam followers 46 and exact price cam followers 56. The cams 35 are shown in the zero position and the vertical gnaph lines indicate the relative positions of the two sets of cam followers with relation to the cams as the cams move to the left in step by step increments. As already indicated above, the length of each cam 35 is equivalent to four steps. Thus, at rest, the exact price cam followers 56a, 56b and 560 are up on their respective cams in the relative positions shown. The corresponding exact price switches 58 are of course closed, while all of the stepping switches 48 are open. Insertion of one nickel, or movement of the cams 35 to the number 1 step position will cause the stepping cam follower 46a to ride up onto cam 35a. It will also be appreciated that earn follower 46a will remain up on cam 35a for only one downward step of the shaft 60 in response to the urging of the subtract cam 80 as previously described.

Similar relative position changes occur with the insertion of other coins. Thus, for example, the insertion of a quarter will cause cam follower 46d to ride up on cam 35d. The 5, 10 and 15 cam followers 46a, 46b, and 460 will of course also be affected :but for different step intervals because of their staggered programming.

Operation of the device 10 may now best be understood by referring to the schematic circuit diagram of FIG. 12. Two representative vending cycles will be described, namely, the insertion of 10 for the purchase of a 10 item, and the insertion of 25 for the purchase of a 10 item with 15 change being returned.

Insertion of a dime or two nickels closes a coin switch which results in the stepping solenoid 16 being energized for two pulses. The cams 35 are moved two steps so that exact price switch 58a is opened While cam followers 46a and 46b ride up on the cams 35a and 35b to the number 2 step position, thereby closing stepping switches 48a and 48b. Price selector switches for each monetary denomination are positioned on the outside of the vending machine, and when the customer selects a 10 article, an electrical circuit is completed through that switch, exact price switch 58b and stepping switch 48b. All circuits through the other stepping, exact price and price selector switches are of course open.

As current flows through the deScribed 10 circuit, the motor M1 and payout relay are energized to start rotation of the subtract cam and payout cam 95. Stepping switch 46b is opened after one downward step of the shaft 60, and since there is a one step time leg in the effect of the payout cam 95, the payout solenoid 126 is de-energized when the first reciprocation of the payout slide occurs. Since the blocking plate limits the movement of the payout slide, no change is returned to the customer.

During the described cycle, the zero switch 54 was also closed. Thus, as the subtract cam 80 is nearing completion of its revolution, the boss 86 thereon closes the reset switch 90 which closes a circuit through a coin re turn relay to energize the stepping solenoid 16. With the repeated opening and closing of the reset interrupter switch 225, the drum 32 continues its uni-directional stepby-step rotation until the zero switch is once again opened to de-energize the stepping solenoid. Suitable circuitry is of course provided for actuating the article vending apparatus, upon completion of the payout cycle. Slug rejector means are likewise provided, but since these elements form no part of the instant invention, detailed discussion thereof has been omitted.

When 25 is inserted, the stepping operations are the same except that the earns 35 are caused to move five steps so that cam followers 46 now occupy the number position. If the customer now closes the price selector switch, the previously described 10 switching circuit is also closed with the same results. Note, however, that the cam follower 46b is in the number 5 position and will therefore remain on its cam 35b until the fourth downward step of the shaft 60. The payout solenoid 126 will therefore be energized for three movements of the payout slide 110 so that three nickels will be re turned as change to the customer.

During both of the described vending cycles, the nickel escrow coil 154 is energized to permit any captive nickels to fall out of the passageway 152 and the table 160 is tilted by the subtract cam actuated escrow cash box drive assembly 180 to drop any monies thereon into the cash box. On the other hand, if the customer manually closes the coin return switch before making a selection, the escrow return solenoid 215 is energized to return any inserted monies to the customer. Of course, if the tube empty switch 138 is open, the empty lights are lit and the payout relay is prevented from being energized. In such a case, the only way merchandise can be vended is if the exact price of the article is inserted. It will thus be noted that the exact price switches 58 function to by-pass the coin tube empty switch when the latter is open to permit purchase of merchandise for exact change only.

It is believed that our invention, its mode of construction and operation, and many of its advantages should be readily understood from the foregoing without further description, and it should also be manifest that while a preferred embodiment of the invention has been shown and described for illustrative purposes, the structural details are nevertheless capable of wide variation within the purview of our invention as defined in the appended claims.

We claim:

1. A coin handling and changing device adapted for use'in a vending machine comprising:

a coin actuated pulse generator,

drive means operative responsive to the pulses emitted by said pulse generator,

a rotatable stepping wheel driven by said driver means in only a single direction and having a plurality of equally spaced steps positioned therearound so that one pulse of said driver means drives said wheel through one of said steps, I

a gang of rotatable stepping cams connected to said wheel for unison rotation therewith,

said stepping cams being related in arcuate length to one of said steps,

a gang of stepping cam followers cooperating one with each of said stepping cams,

stepping switch means associated with said stepping cam followers and adapted to be actuated thereby,

a plurality of manually operated price selector switches,

step subtract means connected to said stepping cam followers and adapted to move said stepping cam followers upon actuation of one of said price selector switches in said single direction in increments of said steps,

coin payout means associated with said step subtract means and operative responsive to said stepping switch means, and

reset means operable upon completion of a payout cycle to return said wheel and cams to the starting position by rotating them in said single direction.

2. The coin handling and changing device of claim 1 which further comprises a coin storage tube,

a gang of exact price cam followers cooperating one with each of said stepping cams,

said stepping cams acting simultaneously upon said stepping cam followers and exact price cam followers, and exact price switch means associated with and adapted to be actuated by said exact price cam followers,

said exact price switch means being effective to prevent a vend cycle when said storage tube is empty unless a price selector switch is actuated which corresponds exactly in price with the amount of money inserted.

3. The coin handling and changing device of claim 1 in which said stepping wheel comprises a ratchet wheel having a plurality of ratchet teeth equally spaced around the circumference thereof, the arcuate distance between each adjacent pair of said teeth comprising one of said steps.

4. The coin handling and changing device of claim 3 in which said driver means comprises .a solenoid having a reciprocable armature, and

a rigid drive arm connected to the free end of said armature,

said drive arm being in constant engagement with said ratchet teeth.

5. The coin handling and changing device of claim 3 in which said gang of stepping cams comprises a cylindrical drum, and

a plurality of camming surfaces projecting outwardly from the surface of said drum,

said drum and ratchet wheel being rotatably mounted on a common longitudinal shaft.

6. The coin handling and changing device of claim 5 in which a zero cam is positioned on the outer surface of said drum,

a zero cam follower cooperating with said zero cam,

and

a zero switch associated with said zero cam follower and adapted to be actuated thereby,

said zero cam follower being up on said zero cam when said ratchet wheel is in said starting position.

7. The coin handling and changing device of claim 6 in which the arcuate length of said stepping cams is equal to four of said steps, and

the arcuate length of said zero cam is equal to one of said steps.

8. The coin handling and changing device of claim 7 in which said cylindrical drum comprises a plurality of individual drum segments each having one of said stepping cams integrally formed thereon, and

a ratchet wheel segment having said ratchet wheel and said zero cam integrally formed thereon,

all of said segments being formed with mating indexing teeth whereby the relative positions of said stepping cams with relation to said zero cam may 'be readily adjusted. 9. The coin handling and changing device of claim 7 in which said step subtract means comprises a rotatable subtract cam having four subtract camming surfaces formed in the periphery thereof,

said subtract camming surfaces successively decreasing in radius from the center of said subtract carn a distance equivalent to one of said steps,

motor means for rotating said subtract cam upon actuation of one of said price selector switches,

a subtract lever having a cam follower spring urged against the periphery of said subtract cam, and

a subtract link pivotally connected at one end thereof to said subtract lever and at the other end thereof to said gang of stepping cam followers, whereby the movement of said subtract lever when urged from one subtract camming surface to the next moves said stepping cam followers one of said steps in said single direction.

10. The coin handling and changing device of claim 9 in which said coin payout means comprises a payout cam mounted on a common shaft with said subtract cam for unison rotation therewith,

said payout cam being formed with four substantially identical camming notches in the periphery thereof adapted to impart a reciprocating motion to a cam follower bearing thereagainst,

a payout lever having a cam follower spring urged against the periphery of said payout cam,

a payout slide operatively engaging said payout lever for reciprocating movement therewith, and

a coin storage tube associated with said slide and adapted to drop a coin onto said slide when said slide is positioned therebeneath,

said payout lever cam follower being positioned so that the same does not bear against the first of said camming notches until said subtract lever cam follower bears against the second of said subtract carnming surfaces.

11. The coin handling and changing device of claim 10 in which a blocking plate is positioned to inhibit the full reciprocating movement of said payout slide and prevent the payout of coins thereby, and

electrical means for retracting said blocking plate,

said electrical means being connected to said stepping switch means.

127 The coin handling and changing device of claim '9 in Which said subtract cam makes one complete revolution for each payout cycle and said reset means comprises a reset switch,

means on said subtract cam automatically actuating said reset switch upon completion of said revolution,

said reset switch being electrically connected to said solenoid and closing a circuit to energize said solenoid, and

a reset interrupter switch cooperating with said drive arm and adapted to be actuated thereby with each stroke of said drive arm so that said armature continues to reciprocate while said solenoid is energized,

said solenoid being de-energized upon actuation of said zero switch when said zero cam reaches said starting position.

13. The coin handling and changing device of claim 9 and further comprising first chute means for receiving up to two unit denomination coins,

second chute means for receiving coins of varying denominations and all unit denomination coins in excess of two,

a coin storage tube associated with said first chute means and adapted to receive said unit denomination coins passing therethrough,

a blocking member norm-ally urged to prevent passage of said unit denomination coins through said first means, and

electrical means operable upon the actuation of one of said price selector switches to withdraw said blocking member and permit passage of said unit denomination coins through said first chute means.

14. The coin handling and changing device of claim 13 in which an escrow table is in communication with said first and second chute means and is adapted to retain coins thereon,

rocker plate means linked to said subtract cam for automatically tilting said plate to drop coins thereon into a cash box upon actuation of one of said price selector switches,

a manually operable return switch,

10 said tube-full sensor being pivotally mounted and adapted to move said angular coin diverter into said first chute means when said tube is full whereby said angular diverter prevents passage of said unit de- 15 nomination coins from said first chute means into said storage tube and causes diversion thereof onto said escrow table.

16. In a coin handling and changing device adapted for 'use with a coin operated vending machine for selectively dispensing one of a plurality of variously priced articles and including coin actuated pulse generator means, a plurality of rotatable stepping cams, stepping cam followers cooperating with said stepping cams, stepping switches associated with and adapted to be actuated by said stepping cam followers, a plurality of customer operated selector switches, coin storage means and change payout means associated with said coin storage means, the improvement comprising drive means for rotating said stepping cams in fixed incremental steps in a single direction only, said drive means being operative responsive to said pulse generator means to add to the relative position of said stepping cams from zero start position a number of steps equal to the number of pulses from said generator means, and

subtract means operative responsive to the actuation of one of said selector switches to move said stepping cam followers in said single direction in increments of said steps to thereby subtract from the number of steps previously added to said stepping cams relative to said stepping cam followers,

said subtract means being opcratively related to said payout means whereby said payout means returns correct change to the customer when the price of the article selected is less than the money inserted into the machine.

17. In the coin handling and changing device of claim 16 the further improvement comprising reset means automatically operable upon completion of operation of said payout means,

said reset means causing said drive means to rotate said stepping cams in said single direction until said cams achieve said zero start position. 18. In the coin handling and changing device of claim 17, the further improvement comprising exact price cam followers cooperating with said stepping cams, and exact price switches associated with and adapted to be actuated by said exact price cam followers,

said stepping cams cooperating simultaneously with said said stepping cam followers and exact price cam followers,

said exact price switches being efiective to prevent initiation of a vending cycle when said coin storage means is empty unless the price of the article selected exactly equals the amount of money inserted.

STANLEY H. TOLLBERG, Primary Examiner. 

